Hydraulic multiplier vehicular system

ABSTRACT

High torque multiplication with ready reversibility and absence of surging are obtained by a pair of oppositely toothed circular rotors fixed to a circular separator therebetween and smoothly rotatably fitted in a co-axial cylindrical chamber and fed by high pressure fluid. The combination of such rotor and chamber is utilized in a system including a clutch drive switchably passing fluid through or past such combination of rotors and rotor chamber and in reversible directions; the preferred system is a vehicle.

Pancoast HYDRAULIC MULTIPLIER VETHCULAR SYSTEM [76] Inventor: Ervin M.Pancoast, Box 242, Vega,

Tex. 79092 [22] Filed: Feb. 20, 1973 21 App]. No.: 333,498

[52] US. Cl. 180/70 R, 180/66 R, 60/493 [51] Int. Cl B60k 17/02 [58]Field of Search 60/493; 416/223; 180/66 R; 180/70 R [56] ReferencesCited v UNITED STATES PATENTS 385,063 6/1888 Lodge et a1 192/671,778,501 10/1930 Lehmann 60/493 2,335,106 11/1943 Carter 416/223 X3,363,709 1/1968 Hukerikar 60/493 X 3,504,776 4/1970 Misenti 192/67 RPrimary ExaminerEdgar W. Geoghegan Assistant Examiner-Wil1iam F. WoodsAttorney, Agent, or Firm-E1y Silverman [5 7] ABSTRACT High torquemultiplication with ready reversibility and absence of surging areobtained by a pair of oppositely toothed circular rotors fixed to acircular separator therebetween and smoothly rotatably fitted in acoaxial cylindrical chamber and fed by high pressure fluid. Thecombination of such rotor and chamber is utilized in a system includinga clutch drive switchably passing fluid through or past such combinationof rotors and rotor chamber and in reversible directions; the preferredsystem is a vehicle.

10 Claims, 11 Drawing Figures gpmmwm sum SHEET 1 [IF 3 PMENTEUJM 91914SHEET 2 [If 3 j//////fl///////fl//////////// ill HYDRAULIC MULTIPLIERVEHICULAR SYSTEM BACKGROUND OF THE INVENTION:

1. THE FIELD OF THE INVENTION:

The fields of the invention are in power transmission of hydraulic'typeusing rotary fluid and in clutches and power steps controls with meansto effect torque reversal.

2. DESCRIPTION OF THE PRIOR ART:

The prior art effected torque multiplication by gear drive rotorselection that theoretically permitted relatively constant speed of adriving motor; however, the gears subjected the motor and/or drivingmechanism to impact stresses that were undesirable and/or damaging;hydraulic multipliers were substantially unidirectional and also subjectto impact action due to surges and lags in correction time. Both typesof structures have involved mechanisms and structures. This inventionprovides safe, inexpensive, reliable torque multiplication withoutundesirable side effects of the prior art apparatuses.

BRIEF DESCRIPTION OF THE DRAWINGS:

FIG. 1 is a top plan diagrammatic view of a vehicle equipped accordingto this invention.

FIG. 2 is an enlarged side and vertical longitudinal sectional veiw ofzone 2A of FIG. 1.

FIG. 3 is a diagrammatic representation of the hydraulic connections ofcomponents shown in FIGS. 2 and 11 and 8.

FIG. 4 is a side view of the selector assembly 45 when unit 46 isoperatively connected to selector assembly input shaft 49 and outputshaft 50.

' FIG. 5 is an interior longitudinal cross-sectional view of theselector assembly in the position of parts shown in FIG. 4.

FIG. 6 is an interior longitudinal cross-sectional view of the selectorassembly 46 in the position of parts thereof wherein the unit 46 isdisconnected from the power source 37 and shafts 49 and 50 for powertransmission therebetween.

FIG. 7 is a side view of the torque multiplier unit 46 along directionof arrow 7A of FIG. 10.

FIG. 8 is a serially broken away view of unit 46 along planes 8A, 8B,8C, 8D, 8E, 8F; planes 8A, 8B, 8C and 8D are shown in FIG. 7; planes 8C,8D and 8E are shown in FIG. 10, planes 8Dm 8E, 8F and 86 are shown inFIG. 9.

FIG. 9 is a side view of the torque multiplier unit 46 along directionof arrow 9A of FIG. 10. v

FIG. 10 is a diagrammatic broken-away view through section 10A-10A ofthe casing of unit 46 to expose the torque multiplier rotor unit whichis shown in end view along direction of arrow 10B of FIG. 8.

FIG. 11 is a perspective broken-away view of the torque multiplier unit46 with casing 90 broken away at section l0A-10A.

DESCRIPTION OF THE PREFERRED- EMBODIMENT:

In general, this overall apparatus is a vehicle with a frame 30, a powersource 37 and a torque multiplier assembly 43.

The frame 30 is rigid and is composed of, firmly joined together, rigidback member 31, a rigid front member 32, a rigid left side member 33 anda rigid right side member 34, with transverse rigid cross members I 36,36' and 36". The frame supports a power source,

internal combustion engine 37, and a transmission 41 and a torquemultiplier assembly 43. The engine 37 drives transmission output shaft39 through a standard variable speed transmission 41; transmission 41operates through a transmission output shaft housing 42. Back rightdrive wheel 21, back left drive wheel 22, front pivotal left wheel 23and front pivotal right wheel 24 are attached to the frame 20 inconventional manner and to a steering wheel 27 which is in the vicinityof a driver 35 and supported on the frame 30 steering post 26. Thetransmission assembly 41 is operatively connected to and powers torquemultiplier assembly 43. Assembly 43 has a converter output shaft 50which is operatively connected to the drive wheels 21 and 22.

A drivers seat is firmly yet adjustably supported on frame 30 and driver35 may sit on seat 25.

The torque multiplier assembly 43 comprises a torque multiplier driveselector assembly 45, a torque multiplier unit 46 and a torquemultiplier control assembly 47 therefor in co-operative combination andfirmly attached to frame 30.

The selector assembly 45, the parts of which are shown in FIGS. 4-6,comprises, in co-operative connection,

a. static members such as a rigid casing 51 and the journal bearings 72and 82,

b. axially rotatable members which are longitudinally fixed, such as therigid cylindrical converter input shaft 49 and the rigid cylindricalconverter output shaft 50 which are rotatably supported in the journalbearings 72 and 82 and sleeve 61; and wheels 60 and 68,

c. longitudinally movable non-rotating members as fork unit 52, and a d.longitudinally and rotatably moving members as sprockets 63 and 71' andsleeve unit 67.

Output shaft 39 of transmission 41 is firmly attached to input shaft 49as by a key 28 in a collar 29.

Casing 51 is firmly fixed to a cross member 36 of frame 30 and to thetransmission 41; a torque multiplier casing 48 is also firmly attachedto transmission 41 and another cross member 36" of the frame 30. Motor37 and transmission 41 are also firmly attached to frame 30.

The group of axially rotatable members includes driven output circulargear wheel 60 and driving input drive gear wheel 68. Gear wheels 60 and68 are coaxial with shafts 50 and 49 respectively and shafts 50 and 49are co-axial. The driven output gear wheel 60 is rotatably supported infixed longitudinal position on the shaft 50 and the input gear drivewheel 68 is rotatably supported in fixed longitudinal position on theinput shaft 49. Collars 60' and 68 each have set screws 60S and 68Srespectively that are firmly seated therein and slidably extend intocircular slots 50S and 49S respectively therefor on shafts 50 and 49respectively. Also, each of the collars 60' and 68' is fixed to thewheels 60 and 61 respectively and locate those wheels in theirlongitudinal position on shafts 50 and 49 respectively therebypermitting those wheels to rotate about those shafts, respectively.

Shaft 50 is provided with an axially or longitudinally extending set ofrigid output splines 73 and axially or longitudinally extending set ofrigid bypass splines 75; the shaft 49 is provided with longitudinallyextending sets of rigid longitudinally extending bypass splines 79 andinput splines 80. Splines of sets 73, 75, 79 and 80 extend radially fromtheir shafts and are the same in size and shape. The set of bypasssplines 75 of shaft 50 are located at the right-hand (as shown in FIG.end of the shaft 50, while the set of output splines 73 of output shaft50 are located spaced leftwardly away therefrom and near the output gearwheel 60, as shown in FIGS. 4 and 5. The set of input splines 80 of theinput shaft are located on the right-hand side of the input shaft, asshown in FIG. 5, while the set of bypass splines 79 of the input shaft49 are located toward the output end 77 of the input shaft (to the left,as shown in FIGS. 5 and 6).

The gear wheels 60 and 68 are driven by the drive plates 61 and 69respectively when the teeth 132 and 134 of those drive plates are movedby the fork unit 52 into engagement with the teeth as 131 and 133 of thewheels 60 and 68 respectively.

The wheels 60 and 68 respectively are operatively connected to powertransmission elements as drive chains 123 and 121 respectively, whichchains are operatively connected to torque multiplier unit output gearwheel 128 and torque multiplier unit input gear wheel 126, respectively.

A rigid longitudinally movable non-rotating fork unit 52 extendslongitudinally of and is slidably attached to the casing 51. Fork unit52 comprises a. a rigid longitudinal spacing bar 56; bar 56 has firmlyattached to its left end thereof (as in FIGS.

b. an output yoke 53, and,

c. at the middle thereof, a sleeve control yoke 54, and

d. at the right end thereof, as shown in FIGS. 4-6, an

input yoke 55, and

e. a control handle 84.

The longitudinally movable non-rotating fork unit 52 is slidablysupported in the brackets 85, 86, 87 and 88 on the rigid casing ceiling81 for longitudinal movement along the length of the casing. Controlhandle 84 is firmly fixed to the bar 56 and extends upward through aslot 83 in ceiling 81 of casing 51. Handle 84 is operatively connectedto an operators control handle 145 through a selector control linkage146.

The control sleeve unit 67 and sprockets 62 and 63 comprise the largelongitudinally movable and also rotatable elements of the assembly 45and are co-axial with the shafts 49 and 50 and rotatably supported Ithereon and movable therealong and are cooperatively connected withthose shafts and the splines thereof.

The control sleeve unit 67 is a hollow rigid cylindrical sleevecomprising a rigid cylindrical longitudinally extending side wall 64Cand end walls 64A and 64B and interior sleeve spline sets 74 and 78.More particularly, a set of longitudinally extending sleeve outputsplines 74 and a like input sleeve spline set 78 are rigidly fixed tothe interior of the cylindrical wall 64C and extend inwardly thereof.The splines of set 74 match with the splines of sets 75 and the splinesof set 78 match with the splines of set 79; by match" is meant havingequal number and size (as measured in transverse section).

Circular flanges 65 and 66 fixed to the outside wall 64C slidably engagefork arm 58 to provide for movement of sleeve unit 67 lengthwise ofcasing 51.

The output sprocket 73 comprises a rigid collar 62 and a toothed driveplate 61 and a flange 62A firmly joined together. The rigid cylindricalcollar 62 is internally grooved to match and accept the splines of theshaft output spline set 73 and is firmly fixed to a toothed circularoutput drive plate 61. A circular flange 62A extends radially from theperiphery of the sprocket body 62 and slidably yet flnnly engages thearms 57 of the yoke 53 whereby the yoke arm 53, sprocket body 62 and thedrive plate 61 move longitudinally of the shaft 50, together with theremainder of the fork unit 52. The drive plate 61 is a rigid circularplate co-axial with shaft 50 and is provided with a plurality ofequi-sized clutch teeth 132 that extend parallel to axis of shaft 50,and in position of parts shown in FIGS. 4 and 5, engage with equallysized and spaced teeth clutch teeth 131 on gear wheel 60. A multiplieroutput continuous drive chain 123 engages the teeth 136 on drive wheel60.

The input sprocket 71 comprises a collar 71, a flange 70 and a tootheddrive plate 69. The collar 71 is a rigid cylindrical body internallygrooved to match and accept the splines of input spline set 80. Thesplines (like 73) slidably engage such grooves in input sprocket body 71(as in sprocket body 62). A circular input sprocket flange 70 extendsradially from and is flnnly fixed to the periphery of the sprocket body71 and slidably engages arm 59 of yoke 55 whereby arm 55, sprocket body71 and plate 69 move longitudinally of shaft 49 together with remainderof the fork unit 52 and other units as 67 and 73 moving therewith.

with shaft 49. The sprocket plate 69 is provided with v clutch teeth 134equal in size and spacing that extend parallel to axis of shaft 49 (and50) and, in position of FIGS. 4 and 5, engage equally sized and spacedclutch teeth 133 on drive gear wheel 68.

A multiplier input continuous chain 121 engages teeth 138 on drive gearwheel 68.

The right-hand (as shown in FIGS. 4-6) input end of shaft 50 has a rigidcylindrical cap 76 that has a smooth sliding fit with interior of sleeve64C and a smooth sliding fit on output end 77 of shaft 49.

Also, the arm 54 is provided with adjustable lock nuts 54A and 54B tolocate roof 81 in fixed spatial relationship to the yoke 58 (which maybe a bearing) and shafts 49 and 50, especially as the casing 51 issufficiently rigid to be dimensionally stable during operation of theassembly 43. Accordingly, shafts 49 and 50 are held coaxial duringoperation of the assembly 43 by sleeve unit 67 and journal bearings 72and 82 and casing 51.

When it is desired to utilize the force multiplication of the unit 46,the handle 84 of fork unit 52 is moved (leftwards as shown in FIGS. 4-6)away from input end, 49A, of the shaft 49. This movement of unit 52 andits arm 54 moves the yoke arms 58, 57 and 59 of the arms 54, 53 and 55,respectively, (to the left, as shown in FIGS. 4-6); on such movement ofunit 52, the yoke arm 58 engages the flanges 65 and 66 on thecylindrical body 64 of the sleeve 67 and the sleeve unit 67 is therebymoved longitudinally (to the left) while still allowed to rotate aboutthe axis of the shafts 49 and 50. In such position, as shown in FIG. 5,the teeth 131 and 132 of the driven sprocket 60 and the sprocket body 63are engaged while the teeth 133 and 134 of the plate 68 and 69,respectively, are also together and engaged with each other. In thisstage of operation, there is power transmission through the gear wheels68 and 60, via drive chains 121 and 123, to anclfrom the unit 46.Accordingly, manipulation of the fork unit handle 84 provides forselective connection of transmission of power from the shaft 49 to theunit 46 to shaft 50 in the position of parts shown in FIG. 5.

In operation of the selector assembly in the position of parts shown inFIGS. 4 and 5, with the control handle 84 moved to the right-hand(input) side of the shaft 49 of the slot 83 in the casing 51, power istransmitted from shaft 49 to the sprocket body 71 through the teeth 134to the teeth 133 through the drive wheel 68 through the input or drivechain 121 to the unit 46. The multiplier output chain 123 transferspower from unit 46 to the drive sprocket gear wheel 60 which is, (exceptfor its attachment to sprocket 63 freely rotatable about the shaft 50)and from such sprocket wheel through its teeth 131 of the plate 60 tothe teeth 132 of the plate 61 to sprocket body 62 and therefrom to thesplines 73 on the shaft 50.

In this position of parts, shown in FIGS. 4 and 5, the output spline set74 of sleeve 67 is moved by fork unit 52 from position thereof in FIG. 6and is disengaged from the bypass spline set 75 on the shaft 50.Similarly, in such position shown in FIG. 5, which condition also existsin the position ofparts shown in FIG. 4, the input spline set 78 (thespline members of which set are firmly attached to the interior of theshell 64 and are firmly attached to such rigid shell) are disengagedfrom the set of bypass splines 79, which spline set is attached to theoutput end of the shaft 49.

When it is not desired to utilize the force multiplication of the unit46, the handle 84 of fork unit 52 is moved (rightwards as shown in FIGS.4-6) toward the input end, 49A, of the shaft 49. This movement of unit52 and its arm 54 moves the yoke arms 58, 57 and 59 of the arms 54, 53and 55, respectively, to the right, as shown in FIGS. 4-6; on suchmovement of unit 52 the yoke arm 58 engages the flanges 65 and 66 on thecylindrical body 64 of the sleeve 67 and the sleeve unit 67 is therebymoved longitudinally to the right and locked to the splines of theshafts 49 and 50. In such position, as shown in FIG. 6, the teeth 131and 132 of the driven sprocket 60 and the sprocket body 63 aredisengaged while the teeth 133 and 134 of the plate 68 and 69,respectively, are also moved apart and disengaged from each other. Atthis stage of operation (shown in FIG. 6), the sets of splines 74 and 75are operatively engaged and the sets of splines 78 and 79 areoperatively engaged whereby power passes from the shaft 49 through theset of splines 79 to the shell 64C to the splines of set 75, affixed tothe shaft 50, and through shaft 50 to the output end of the shaft 50.

In this operation, there is a disengaging of power transmission throughthe gear wheels 68 and 60 via the chain drive 121 and 123 to the unit46. Accordingly, manipulation of the fork unit handle 84 provides forselective disconnection of transmission of power from the shaft 49 tothe unit 46 in the position of part shown in FIG. 6 and then providesfor direct transmission of power from input shaft 49 to output shaft 50.

In operation of the selector assembly 45 in the position of parts shownin FIG. 6, with the control handle 84 moved to the right (input) side ofthe shaft 49 and of the slot 83 in the casing 51, power is transmittedfrom shaft 49 past the sprocket body 71 and the teeth 134 and the teeth133 of the drive wheel 68 and past but not through the input or drivechain 121 to the unit 46. The multiplier output chain 123 then transfersno power from unit 46 to the driven sprocket gear wheel 60 or teeth 131and the teeth 132 of the plate 61 to sprocket body 62 and therefrom tothe splines 73 on the shaft 50.

In this position of parts, shown in FIG. 6, the output spline set 74 ofsleeve 67 is moved by fork unit 52 from position thereof in FIGS. 4 and5 and is engaged with the bypass spline set 75 on the shaft 50.Similarly, in such position shown in FIG. 6, the input spline set 78 isengaged with the set of bypass splines 79, which spline set is attachedto the output end of the shaft 49.

The torque multiplier unit 46 comprises a rigid rotor casing 90, a rotor89, shaft 99, and gears 106 and 107. The casing comprises an upperchamber wall 91, a lower chamber wall 97, both of which are rigid andimperforate, and a cylindrical side wall 98 with the walls 91, 97 and 98firmly joined together to enclose a rotor chamber 100.

The rotor 89 comprises a rigid flat cylindrical top rotor wall 92, a toprigid counter-clockwise toothed body 93, an intermediate rigid flatcylindrical rotor wall 94, a bottom rigid clockwise toothed body and abottom flat cylindrical rotor wall 96. The elements 92-96 and shaft 99therefor are all firmly joined to gether as by screws 109, 109 and 109".The walls 92, 94 and 96 are flat thin rigid disks of the same thicknessand diameter with an exterior diameter forming a close fit to theinterior of the circular cylindrical wall 98. A free sliding fit isprovided between the adjacent flat surfaces of rotor wall 92 and casingwall 91, and between adjacent flat surfaces of walls 96 and 97. Walls92, 94 and 96 are generally imperforate.

Shaft 99 is rotatably supported in journals 118 and 119 and drives aright angle bevel gear 106; gear 106 engages bevel gear 107; gear 107drives output shaft 108; shaft 108 and gear 107 are rotatably supportedin gear casing 117. Gear casing 117 is firmly fixed to outside of rotorcasing 90.

Shell 48 of assembly 48 is a rigid cup-shaped casing with bottom wall156, rear wall 157, front wall 158 and side walls which enclose andsurround a chamber 159 wherein are located the rotor assembly 46,brackets as 151-153 and gears 126 and 128. Bracket 151 supports gearcasing 117. Bracket 152 supports, on a journal bearing 152', outputshaft 108; bracket 153 supports a journal bearing 155 for shafts 108 and129; brackets 154 and 154 support housing of hydraulic pump 122. Shaft108 is operatively connected to and drives output gear wheel 128; wheel128 engages chain 123. Gear wheel shaft 129 is supported in journals 155and 155' and is driven by gear wheel 126 and drives the rotor ofhydraulic pump 122. Pump 122 is connected by output line 149 throughvalve casing 148 and valve body 142 and input lines 101 or 111 to rotorcasing 90; rotor discharge lines and are operatively connected to valvecasing 148 of reversing valve 150 and therethrough to discharge line 130which leads to hydraulic sump 141. Sump 141 is connected by hydraulicinlet line 139 to inlet of pump 122. An adjustable relief valve 140 isoperatively connected across outlet line 149 to discharge line 130.

An inlet line 101 passes through a rigid transition body 102 firmlyaffixed to the chamber side wall 98 of rotor casing 90 and has a conduittherethrough 103 which enters into rotor chamber 100 located between thewalls 91, 96 and 98. A second inlet line 111 is operatively joined to atransition piece 112 which is firmly joined to the chamber wall 98. Thetransition piece 1 12 has a conduit 113 continuous with both the passagewithin line 111 and rotor chamber 100. Conduit 103 and conduit 113 eachenter chamber 100 tangent to the portion of the chamber 100 whereintoothed bodies 93 and 95 respectively are located, as shown in FIGS. 7,8 and 9 and parallel to those bodies.

A top counterclockwise outlet line 105 is joined to an outlet transitionpiece body 104 which has a conduit therein which is at the same level asand parallel to the top counterclockwise toothed rotor body 93. A bottomclockwise outlet line 115 is operatively joined to the transition body114 (which body 114 is a mirror image of the transition piece 112) andwhich has its opening into the chamber 100 at the same level as andparallel to the body of the bottom, clockwise toothed rotor 95. Conduits105 and 115 leave chamber 100 tangent to the portion of chamber 100wherein the toothed bodies 93 and 95, respectively, are located. Thepoint of entry of conduit 103 and exit of conduit 115 are, at the samerelative radial position as are the same points of conduits 113 and 105,as shown in FIGS. 7-11.

The control assembly 47 is actuated by a conventional car or tractorelectric storage automotive battery 40 and, through a switch 44,supported on frame 30, actuates either of valve pilots 143 or 144 tomove the valve body 142 to direct hydraulic fluid under pressure frompump 122 to rotor casing 90 to drive the rotor 89 either clockwise orcounterclockwise, as seen from above in FIG. 8. Valve 150 may be handactuated.

The switch 44 and bell crank 145 are located on vehicle in the immediatevicinity of the driver seat and wheel 27 so that the driver may alsomanipulate the switch 44 and/or crank 145. Bell cranks 145 and 146 arepivotally yet firmly supported on frame 30 as are rotor casing 90 andselector assembly casing 51. Shell 48 is firmly attached to casing oftransmission 41 and a cross member as 36' while selector casing 51 isfirmly attached to the frame 30.

The rotor casing 90 is in part supported on shell 48 but may be madesufficiently large to have separate attachment to cross member 36 orother members of frame 30. The valve 150 is firmly supported on frame 30or on rotor casing 90, as shown in FIGS. 2 and 11.

Manipulation of fork handle 84 is accordingly effected by an operator ason seat 25 through a control handle as 145 through a link train, asrigid bell crank 145 pivotally supported on frame 30 and pivotallyconnected to one end of a rigid link arm 148, its other end in turnpivotally connected to one end of a rigid bell crank 146 pivotallysupported on frame 30 and pivotally connected at its other end to oneend of a rigid link arm 147, the other end of which is pivotallyconnected to fork unit handle 84. Handle 84 is slidably located byflanged locking members as 54A and 54B and rod 56 to move along thelength of casing 51 but not transversely to such length. Handle 84 maybe hand actuated directly.

Accordingly, the driver 25 may pass mechanical power from engine as 37directly to shaft 50 in the position of parts of selector assembly 45shown in FIG. 6; alternatively, the driver may pass engine power to thetorque multiplier unit 46 by manipulating the fork unit 52, as bycontrol assembly 47, to provide the array of components of the selectorassembly shown in FIGS. 4 and 5, and thereby, as above described, passpower from engine 37 via drive wheel 68 to torque multiplier unit 46.The torque multiplier unit 46 because of the much greater distance of a.the center of areas over which the force of the hydraulic power of thehigh pressure hydraulic fluid of pump 122 is applied, as area 124 oftooth 129 of toothed body 93, from the center of rotation of that body,as shaft 99 (in journal bearings 118 and 119) than b. the lesserdistance of the center of shaft 99 to the center of area of contact ofgears 106 and 107, provides a greatly increased output torque at shaft108. Such output torque is far greater than the input torque provided atshaft 129 (which is firmly connected to driver gear wheel 126 to drivepump 122) or shaft 49. Such increased torque is provided by shaft 108 todrive gear wheel 128, which is firmly attached to shaft 108, a rigidstrong shaft, and passed by the continuous chain 123 to gear wheel 60and, in position of parts shown in FIGS. 4 and 5, as above described, tooutput shaft 50. For a large conventional tractor of 250 horse poweroutput the internal diameter of rotor casing would be 3 to 4 feet whilethe center line of contact of bevel gears 106 and 107 would be only from1 to 3 inches, and usually 1% inch. The fit of each of the toothedbodies 93 and in walls 92, 94, 96 could be 0.002 inch or as high as0.010 inch if made, for instance, by rip saw blades or like uniformlycusped or cupped peripheral cut out zones, as 127, or depth 5 to 10percent of the radius of the rotor case internal diameter. Such spacing(of 0.002 to 0.010 inch) permits avoidance of impact shocks because suchstructure permits escape or bleeding of high pressure liquid throughsuch spacings when a mechanical block is met and so avoids undue strainon the wheel drive axles, as and 125 (respectively operatively joined towheels 22 and 21). Bodies 93 and 95 are identical in size and similar inshape but are oppositely turned mirror images, as shown in FIGS. 8 and11, as the teeth as 127 and 127' are oppositely directed on bodies 93and 95.

Each of the toothed bodies 93 and 95 is a rigid circular metal bodycoaxial about shaft 99, each with a plurality of like cutaway zones, as127, at the periphery thereof, much as in the shape of a circularripsaw, Each zone as 127 has a concave surface, as 124, concave indirection from which fluid is applied thereagainst, as by flow fromorifice 103 of conduit 101, in case of body 93, and from orifice 113 ofconduit 111 in case of body 95; each such tooth, as 129, is convex onthe opposite side, as 110: The term concave does not mean only curvedlyshaped, but includes a. an acute angled hollow comer, as 164 (FIG. 11)

and 164' and the adjacent straight edges, as 163 and 165'; and

b. an obtuse angled hollow corner, as 162 or 162' and the adjacentstraight edges, as 167' and 163 (FIG. 8).

Each body, as 93, includes vanes, as 129, and a central portion 93 towhich the vanes and shaft 99 are firmly attached. The term concave asherein used does not mean only curvedly shaped but includes an obtusesolid corner, as 166 or 166 and the adjacent straight edges, as 165 and167. For each of the vanes or teeth, as 129 and 129, a line 168 and 170(FIG. 8) halfway between the front or leading convex edge 110 or 167 andthe rear or trailing concave edge, as 124 or 165, that is at an acuteangle 171 to the radius, 169, connecting the edge of the tooth to thecenter of rotation, as center of shaft 99, of the vaned body 93; theangle 171 extends to the side of the radius distant from the source offluid applied against the vane, as fluid from line 101 against vanes as129 of body 93 and, for angle 171, fluid from line 111 against vanes as129' of vaned or toothed body 95.

Such shape provides that when the pressure in chamber 100 does rise to adegree indicating a full stoppage is met, the overflow from one point as160 at teeth of body 93 is smoothed out by the surfaces as 161 of theteeth on the other toothed body, as 95, whereby surges are eliminatedand, when the obstacle is passed, or greater power applied by motor 37to chain 121, a smooth return to a driving operation by the action ofthe hydraulic liquid 160' on the concave surfaces facing such fluidstream is accomplished without any further surge and resulting harmfulimpact. The thickness of the body 93 (like 95) would be one-eighth to 1inch, plates 92, 94 and 96 also one-eighth to one-fourth inch for a 3foot internal diameter rotor casing 90. For smaller machines, a rotorcasing of 8 inch internal diameter, one-eighth to one-fourth inch thickbodies 93 and 95, plates 92, 94, 96 of one-sixteenth to one-eighth in.thick, and rubber belts and sheaves instead of chain and gear wheels areused.

This structure 46 thus avoids the problem of surging met withconventional relief valves as 140 which have defininte pressuredifferentials between (a) pressure for such valve to close after beingopened and (b) pressure to open after being closed, with resultingsurging action.

With this apparatus and system, the operator may also, by manipulationof control assembly 47 move valves body 148 to change flow of fluid, as160 a. from pump 122 to rotor chamber 100 to drive the rotor 90counterclockwise, i.e., providing flow from pump 122 via line 101 intochamber 100 and then driving fluid along conduit 101 and against teethor vanes 129 to drive rotor 89 counterclockwise and thence via line 105to sump 141 to b. from pump 122 to valve 150 to line 111, to drive rotor89 clockwise and return fluid via line 115 to valve 150 and sump 141, asshown in FIG. 3. The same high torque is obtained with lack of surgingas described above for the operation of rotor 89 counterclockwise.

Gears 106 and 107 may be helical or hypoid although, for purpose ofillustration, are shown as straight toothed bevel gears.

The apparatus 43 comprising clutch assembly 45, selector assembly 46 andcontrol assembly 47 may be used to transmit power from a motor to anirrigation pump, the motor being attached to shaft 49, the drive of theoutput shaft 50 of assembly 43 being attached to the drive shaft of thepump, as, but not limited to, in US. Pat. No. 3,335,791.

The fluid 160' is preferably a conventional hydraulic liquidtransmission fluid as used in automobile hydraulic transmissions andhydraulic power systems. However, the use of gases, as well as liquidsas a power transmission means is intended to drive the rotor 89. A fitof 0.002 or 0.0l0 inch means a spacing of 0.002 and 0.010 inch,respectively.

I claim: 1. A vehicular apparatus comprising a frame, a power source anddrive wheels, said power source supported on said frame, a power sourceoutput shaft operatively connected to said power source, said frame inpart supported on said drive wheels, and a first power transmission anda wheel drive shaft between said wheels and said power source andoperatively connected thereto, and a torque multiplier assembly, saidtorque multiplier assembly having a torque multiplier assembly inputshaft and a torque multiplier assembly output shaft, said torquemultiplier assembly input shaft operatively connected to saidtransmission means, said transmission means having an input shaftoperatively connected to said power source output shaft, said torquemultiplier assembly output shaft operatively connected to said wheeldrive shaft,

said torque multiplier assembly comprising, in operative combination, 1.a selective transmission assembly with an input and output shaft; 2. atorque multiplier unit with an input shaft and an output shaft; and 3. aselector control assembly, first power transmission means between saidselective transmission assembly input shaft and said torque multiplierunit input shaft and operatively connected to said torque multiplierunit input shaft and to said selective transmission assembly inputshaft, and second power transmission means between said selectivetransmission assembly output shaft and said torque multiplier unit andoperatively connected to said torque multiplier unit output shaft and tosaid selective transmission assembly output shaft, said selector controlassembly comprising a movable control means operatively connected tosaid selective transmission assembly, v

said selective transmission assembly first input shaft means operativelyconnected to said power source, and said selector control meansoperatively connected to said first and second power transmission meansbetween said torque multiplier input and output shafts and to saidselective transmission assembly input and output shafts and movable intoeither of two positions alternatively operatively connecting said inputshaft of said selective transmission assembly directly to the selectivetransmission assembly output shaft or to said torque multiplier unitinput shaft,

said torque multiplier unit comprising a fixed rigid rotor casing and arotor chamber within said rotor casing and a rotor assembly rotatablysupported in said chamber in said rotor casing,

said casing having a cylindrical interior surface,

said rotor assembly comprising a first vaned rotor body having concaveradial pockets each with concavity directed in one tangential direction,and each of said pockets having a convex pocket wall with convexitydirected in a second tangential direction opposite to said onetangential direction,

a second rotor body having concave radial pockets directed in anopposite direction to said one tangential direction and having aconcavity directed opposite to said one tangential direction and each ofsaid pockets on said second rotor body having a convex pocket wall withconvexity directed parallel to said one tangential direction,

said first and second rotors mounted on a common rotor shaft, said rotorshaft rotatably mounted in said rotor casing and firmly fixed to each ofsaid rotor bodies and to a separator between said first and secondrotors, the outer edge of said separator being in loose sliding contactwith the interior of said casing, said separator being a solid flatrigid disc,

the separator having an outer edge closer to said interior casingsurface than the radial edges of the rotors;

each of said rotor bodies comprising a rigid central flat portion and aplurality of like rigid vanes, each vane firmly attached to said centralportion and extending radially therefrom and directed radially andtangentially thereto, each vane having a convex front edge and a concavetrailing edge, with pockets defined by the front edges and trailingedges of adjacent vanes on the same rotor, each of said pockets open atthe radial edges of said rotor vanes, the front and rear edges of eachvane rotor body extending in a direction at the same angle to a linetangent to the radial edges of said vane, the edges of each vane on thesecond rotor body extending at an angle to a line tangent to the radialedges of said vane opposite in direction to the direction of extensionof the vanes on the first rotor, and power transmission means attachedto and extending between said rotor shaft and said torque multiplierassembly output shaft drive means and operatively connecting them,

said torque multiplier unit having a hydraulic pump means comprising apower input means, a hydraulic input line and a hydraulic output line,said hydraulic output line being operatively connected via a pluralityof hydraulic conduit lines to said rotor chamber, one of said hydraulicconduit lines leading into said rotor chamber in a path directed in afirst direction at the vanes of one rotor body and another of saidconduit lines connected to said rotor chamber in a path directed in anopposite direction to said first direction at the vanes of the secondrotor body,

and hydraulic discharge lines from said rotor chamber to a hydraulicsump chamber, and a hydraulic conduit line from said hydraulic sump tothe inlet of said hydraulic pump,

and said first power transmission means from said selective transmissionassembly input shaft operatively connecting to the power input means forsaid pump and the fit of said rotors in said casing chamber has aspacing therebetween of 0.002 to 0.010 inch whereby, when pressure insaid rotor chamber rises to a predetermined degree, hydraulic liquidflows over concave vane surfaces to and between said rotor and saidcasing to convex vane surfaces on the second rotor.

2. Apparatus as in claim 1 wherein said rotor casing has opposingparallel flat side walls and a cylindrical end wall enclosing a rotorchamber, said rotor assembly in said chamber and including a second flatseparator disk between one rotor body and one adjacent rotor casing sidewall and a third flat separator disk between another rotor body and anadjacent rotor casing side wall opposite to said first side wall, saidsecond and third separators each having an outer edge closer to thecylindrical interior casing surface than the radial edges of the rotorbodies.

3. Apparatus as in claim 2 wherein all the vaned pockets in one rotorare of the same shape and size.

4. Apparatus as in claim 3 wherein all the vanes and pockets in thesecond rotor are of the same shape and size on that rotor.

5. Apparatus as in claim 4 wherein the vanes and pockets on both thefirst and second rotors are of the same shape and size.

6. A torque multiplier assembly comprising, in operative combination,

1. a selective transmission assembly with an input and output shaft;

2. a torque multiplier unit with an input shaft and an output shaft; and

3. a selector control assembly, first power transmission means betweensaid selective transmission assembly input shaft and said torquemultiplier unit input shaft and operatively connected to said torquemultiplier unit input shaft and to said selective transmission assemblyinput shaft, and second power transmission means between said selectivetransmission assembly output shaft and said torque multiplier unit andoperatively connected to said torque multiplier unit output shaft and tosaid selective transmission assembly output shaft,

said selector control assembly comprising a movable control meansoperatively connected to said selective transmission assembly,

said selective transmission assembly first input shaft means operativelyconnected to said power source, and said selector control meansoperatively connected to said first and second power transmission meansbetween said torque multiplier input and output shafts and to saidselective transmission assembly input and output shafts and movable intoeither of two positions alternatively operatively connecting said inputshaft of said selective transmission assembly directly to the selectivetransmission assembly output shaft or to said torque multiplier unitinput shaft,

said torque multiplier unit comprising a fixed rigid rotor casing and arotor chamber within said rotor casing and a rotor assembly rotatablysupported in said chamber in said casing having a cylindrical interiorsurface,

said rotor assembly comprising a first vaned rotor body having concaveradial pockets each with concavity directed in one tangential direction,and each of said pockets having a convex pocket wall with convexitydirected in a second tangential direction opposite to said onetangential direction,

a second rotor body having concave radial pockets directed in anopposite direction to said one tangential direction and having aconcavity directed opposite to said one tangential direction and each ofsaid pockets on said second rotor body having a convex pocket wall withconvexity directed parallel to said one tangential direction,

said first and second rotors mounted on a common rotor shaft, said rotorshaft rotatably mounted in said rotor casing and firmly fixed to each ofsaid rotor bodies and to a separator between said first and secondrotors, the outer edge of said separator being in loose sliding contactwith the interior of said casing, said separator being a solid flatrigid disc,

the separator having an outer edge closer to said interior casingsurface than the radial edges of the rotors;

each of said rotor bodies comprising a rigid central flat portion and aplurality of like rigid vanes, each vane firmly attached to said centralportion and extending radially therefrom and directed radially andtangentially thereto, each vane having a convex front edge and a concavetrailing edge; with pockets defined by the front edges and trailingedges of adjacent vanes on the same rotor, each of said pockets open atthe radial edges of said rotor vanes, the front and rear edges of eachvane rotor body extending in a direction at the same angle to a linetangent to the radial edges of said vane, the edges of each vane on thesecond rotor body extending at an angle to a line tangent to the radialedges of said vane opposite in direction to the direction of extensionof the vanes on the first rotor, and power transmission means attachedto and extending between said rotor shaft and said torque multiplierassembly output shaft drive means and operatively connecting them, 1

said torque multiplier unit having a hydraulic pump means comprising apower input means, a hydraulic input line and a hydraulic output line,said hydraulic output line being operatively connected via a pluralityof hydraulic conduit lines to said rotor chamber, one of said hydraulicconduit lines leading into said rotor chamber in a path directed in afirst direction at the vanes of one rotor body and another of saidconduit lines connected to said rotor chamber in a path directed in anopposite direction to said first direction at the vanes of the secondrotor body,

and hydraulic discharge lines from said rotor chamber to a hydraulicsump chamber, and a hydraulic conduit line from said hydraulic sump tothe inlet of said hydraulic pump,

and said first power transmission means from said selective transmissionassembly input shaft operatively connecting to the power input means forsaid pump and the fit of said rotors in said casing chamber has aspacing therebetween of 0.002 to 0.010 inch whereby, when pressure insaid rotor chamber rises to a predetermined degree, hydraulic liquidflows over concave vane surfaces to and between said rotor and saidcasing to convex vane surfaces on the second rotor.

7. Apparatus as in claim 6 wherein said rotor casing has opposingparallel flat side walls and a cylindrical end wall enclosing a rotorchamber, said rotor assembly in said chamber and including a second flatseparator disk between one rotor body and one adjacent rotor casing sidewall and a third flat separator disk between another rotor body and anadjacent rotor casing side wall opposite to said first side wall, saidsecond and third separators each having an outer edge closer to thecylindrical interior casing surface than the radial edges of the rotorbodies.

8. Apparatus as in claim 7 wherein all the vaned pockets in one rotorbody are of the same shape and size.

9. Apparatus as in claim 8 wherein all the vanes and pockets in thesecond rotor body are of the same shape and size on that rotor body.

10. Apparatus as in claim 9 wherein the vanes and pockets on both thefirst and second rotor bodies are of the same shape and size.

1. A vehicular apparatus comprising a frame, a power source and drivewheels, said power source supported on said frame, a power source outputshaft operatively connected to said power source, said frame in partsupported on saiD drive wheels, and a first power transmission and awheel drive shaft between said wheels and said power source andoperatively connected thereto, and a torque multiplier assembly, saidtorque multiplier assembly having a torque multiplier assembly inputshaft and a torque multiplier assembly output shaft, said torquemultiplier assembly input shaft operatively connected to saidtransmission means, said transmission means having an input shaftoperatively connected to said power source output shaft, said torquemultiplier assembly output shaft operatively connected to said wheeldrive shaft, said torque multiplier assembly comprising, in operativecombination,
 1. a selective transmission assembly with an input andoutput shaft;
 2. a torque multiplier unit with an input shaft and anoutput shaft; and
 3. a selector control assembly, first powertransmission means between said selective transmission assembly inputshaft and said torque multiplier unit input shaft and operativelyconnected to said torque multiplier unit input shaft and to saidselective transmission assembly input shaft, and second powertransmission means between said selective transmission assembly outputshaft and said torque multiplier unit and operatively connected to saidtorque multiplier unit output shaft and to said selective transmissionassembly output shaft, said selector control assembly comprising amovable control means operatively connected to said selectivetransmission assembly, said selective transmission assembly first inputshaft means operatively connected to said power source, and saidselector control means operatively connected to said first and secondpower transmission means between said torque multiplier input and outputshafts and to said selective transmission assembly input and outputshafts and movable into either of two positions alternativelyoperatively connecting said input shaft of said selective transmissionassembly directly to the selective transmission assembly output shaft orto said torque multiplier unit input shaft, said torque multiplier unitcomprising a fixed rigid rotor casing and a rotor chamber within saidrotor casing and a rotor assembly rotatably supported in said chamber insaid rotor casing, said casing having a cylindrical interior surface,said rotor assembly comprising a first vaned rotor body having concaveradial pockets each with concavity directed in one tangential direction,and each of said pockets having a convex pocket wall with convexitydirected in a second tangential direction opposite to said onetangential direction, a second rotor body having concave radial pocketsdirected in an opposite direction to said one tangential direction andhaving a concavity directed opposite to said one tangential directionand each of said pockets on said second rotor body having a convexpocket wall with convexity directed parallel to said one tangentialdirection, said first and second rotors mounted on a common rotor shaft,said rotor shaft rotatably mounted in said rotor casing and firmly fixedto each of said rotor bodies and to a separator between said first andsecond rotors, the outer edge of said separator being in loose slidingcontact with the interior of said casing, said separator being a solidflat rigid disc, the separator having an outer edge closer to saidinterior casing surface than the radial edges of the rotors; each ofsaid rotor bodies comprising a rigid central flat portion and aplurality of like rigid vanes, each vane firmly attached to said centralportion and extending radially therefrom and directed radially andtangentially thereto, each vane having a convex front edge and a concavetrailing edge, with pockets defined by the front edges and trailingedges of adjacent vanes on the same rotor, each of said pockets open atthe radial edges of said rotor vanes, the front and rear edges of eachvane rotor body extending in a direction at tHe same angle to a linetangent to the radial edges of said vane, the edges of each vane on thesecond rotor body extending at an angle to a line tangent to the radialedges of said vane opposite in direction to the direction of extensionof the vanes on the first rotor, and power transmission means attachedto and extending between said rotor shaft and said torque multiplierassembly output shaft drive means and operatively connecting them, saidtorque multiplier unit having a hydraulic pump means comprising a powerinput means, a hydraulic input line and a hydraulic output line, saidhydraulic output line being operatively connected via a plurality ofhydraulic conduit lines to said rotor chamber, one of said hydraulicconduit lines leading into said rotor chamber in a path directed in afirst direction at the vanes of one rotor body and another of saidconduit lines connected to said rotor chamber in a path directed in anopposite direction to said first direction at the vanes of the secondrotor body, and hydraulic discharge lines from said rotor chamber to ahydraulic sump chamber, and a hydraulic conduit line from said hydraulicsump to the inlet of said hydraulic pump, and said first powertransmission means from said selective transmission assembly input shaftoperatively connecting to the power input means for said pump and thefit of said rotors in said casing chamber has a spacing therebetween of0.002 to 0.010 inch whereby, when pressure in said rotor chamber risesto a predetermined degree, hydraulic liquid flows over concave vanesurfaces to and between said rotor and said casing to convex vanesurfaces on the second rotor.
 2. a torque multiplier unit with an inputshaft and an output shaft; and
 2. Apparatus as in claim 1 wherein saidrotor casing has opposing parallel flat side walls and a cylindrical endwall enclosing a rotor chamber, said rotor assembly in said chamber andincluding a second flat separator disk between one rotor body and oneadjacent rotor casing side wall and a third flat separator disk betweenanother rotor body and an adjacent rotor casing side wall opposite tosaid first side wall, said second and third separators each having anouter edge closer to the cylindrical interior casing surface than theradial edges of the rotor bodies.
 2. a torque multiplier unit with aninput shaft and an output shaft; and
 3. Apparatus as in claim 2 whereinall the vaned pockets in one rotor are of the same shape and size.
 3. aselector control assembly, first power transmission means between saidselective transmission assembly input shaft and said torque multiplierunit input shaft and operatively connected to said torque multiplierunit input shaft and to said selective transmission assembly inputshaft, and second power transmission means between said selectivetransmission assembly output shaft and said torque multiplier unit andoperatively connected to said torque multiplier unit output shaft and tosaid selective transmission assembly output shaft, said selector controlassembly comprising a movable control means operatively connected tosaid selective transmission assembly, said selective transmissionassembly first input shaft means operatively connected to said powersource, and said selector control means operatively connected to saidfirst and second power transmission means between said torque multiplierinput and output shafts and to said selective transmission assemblyinput and output shafts and movable into either of two positionsalternatively operatively connecting said input shaft of said selectivetransmission assembly directly to thE selective transmission assemblyoutput shaft or to said torque multiplier unit input shaft, said torquemultiplier unit comprising a fixed rigid rotor casing and a rotorchamber within said rotor casing and a rotor assembly rotatablysupported in said chamber in said casing having a cylindrical interiorsurface, said rotor assembly comprising a first vaned rotor body havingconcave radial pockets each with concavity directed in one tangentialdirection, and each of said pockets having a convex pocket wall withconvexity directed in a second tangential direction opposite to said onetangential direction, a second rotor body having concave radial pocketsdirected in an opposite direction to said one tangential direction andhaving a concavity directed opposite to said one tangential directionand each of said pockets on said second rotor body having a convexpocket wall with convexity directed parallel to said one tangentialdirection, said first and second rotors mounted on a common rotor shaft,said rotor shaft rotatably mounted in said rotor casing and firmly fixedto each of said rotor bodies and to a separator between said first andsecond rotors, the outer edge of said separator being in loose slidingcontact with the interior of said casing, said separator being a solidflat rigid disc, the separator having an outer edge closer to saidinterior casing surface than the radial edges of the rotors; each ofsaid rotor bodies comprising a rigid central flat portion and aplurality of like rigid vanes, each vane firmly attached to said centralportion and extending radially therefrom and directed radially andtangentially thereto, each vane having a convex front edge and a concavetrailing edge; with pockets defined by the front edges and trailingedges of adjacent vanes on the same rotor, each of said pockets open atthe radial edges of said rotor vanes, the front and rear edges of eachvane rotor body extending in a direction at the same angle to a linetangent to the radial edges of said vane, the edges of each vane on thesecond rotor body extending at an angle to a line tangent to the radialedges of said vane opposite in direction to the direction of extensionof the vanes on the first rotor, and power transmission means attachedto and extending between said rotor shaft and said torque multiplierassembly output shaft drive means and operatively connecting them, saidtorque multiplier unit having a hydraulic pump means comprising a powerinput means, a hydraulic input line and a hydraulic output line, saidhydraulic output line being operatively connected via a plurality ofhydraulic conduit lines to said rotor chamber, one of said hydraulicconduit lines leading into said rotor chamber in a path directed in afirst direction at the vanes of one rotor body and another of saidconduit lines connected to said rotor chamber in a path directed in anopposite direction to said first direction at the vanes of the secondrotor body, and hydraulic discharge lines from said rotor chamber to ahydraulic sump chamber, and a hydraulic conduit line from said hydraulicsump to the inlet of said hydraulic pump, and said first powertransmission means from said selective transmission assembly input shaftoperatively connecting to the power input means for said pump and thefit of said rotors in said casing chamber has a spacing therebetween of0.002 to 0.010 inch whereby, when pressure in said rotor chamber risesto a predetermined degree, hydraulic liquid flows over concave vanesurfaces to and between said rotor and said casing to convex vanesurfaces on the second rotor.
 3. a selector control assembly, firstpower transmission means between said selective transmission assemblyinput shaft and said torque multiplier unit input shaft and operativelyconnected to said torque multiplier unit input shaft and to saidselective transmission assembly input shaft, and second powertransmission means between said selective transmission assembly outputshaft and said torque multiplier unit and operatively connected to saidtorque multiplier unit output shaft and to said selective transmissionassembly output shaft, said selector control assembly comprising amovable control means operatively connected to said selectivetransmission assembly, said selective transmission assembly first inputshaft means operatively connected to said power source, and saidselector control means operatively connected to said first and secondpower transmission means between said torque multiplier input and outputshafts and to said selective transmission assembly input and outputshafts and movable into either of two positions alternativelyoperatively connecting said input shaft of said selective transmissionassembly directly to the selective transmission assembly output shaft orto said torque multiplier unit input shaft, said torque multiplier unitcomprising a fixed rigid rotor casing and a rotor chamber within saidrotor casing and a rotor assembly rotatably supported in said chamber insaid rotor casing, said casing having a cylindrical interior surface,said rotor assembly comprising a first vaned rotor body having concaveradial pockets each with concavity directed in one tangential direction,and each of said pockets having a convex pocket wall with convexitydirected in a second tangential direction opposite to said onetangential direction, a second rotor body having concave radial pocketsdirected in an opposite direction to said one tangential direction andhaving a concavity directed opposite to said one tangential directionand each of said pockets on said second rotor body having a convexpocket wall with convexity directed parallel to said one tangentialdirection, said first and second rotors mounted on a common rotor shaft,said rotor shaft rotatably mounted in said rotor casing and firmly fixedto each of said rotor bodies and to a separator between said first andsecond rotors, the outer edge of said separator being in loose slidingcontact with the interior of said casing, said separator being a solidflat rigid disc, the separator having an outer edge closer to saidinterior casing surface than the radial edges of the rotors; each ofsaid rotor bodies comprising a rigid central flat portion and aplurality of like rigid vanes, each vane firmly attached to said centralportion and extending radially therefrom and directed radially andtangentially thereto, each vane having a convex front edge and a concavetrailing edge, with pockets defined by the front edges and trailingedges of adjacent vanes on the same rotor, each of said pockets open atthe radial edges of said rotor vanes, the front and rear edges of eachvane rotor body extending in a direction at tHe same angle to a linetangent to the radial edges of said vane, the edges of each vane on thesecond rotor body extending at an angle to a line tangent to the radialedges of said vane opposite in direction to the direction of extensionof the vanes on the first rotor, and power transmission means attachedto and extending between said rotor shaft and said torque multiplierassembly output shaft drive means and operatively connecting them, saidtorque multiplier unit having a hydraulic pump means comprising a powerinput means, a hydraulic input line and a hydraulic output line, saidhydraulic output line being operatively connected via a plurality ofhydraulic conduit lines to said rotor chamber, one of said hydraulicconduit lines leading into said rotor chamber in a path directed in afirst direction at the vanes of one rotor body and another of saidconduit lines connected to said rotor chamber in a path directed in anopposite direction to said first direction at the vanes of the secondrotor body, and hydraulic discharge lines from said rotor chamber to ahydraulic sump chamber, and a hydraulic conduit line from said hydraulicsump to the inlet of said hydraulic pump, and said first powertransmission means from said selective transmission assembly input shaftoperatively connecting to the power input means for said pump and thefit of said rotors in said casing chamber has a spacing therebetween of0.002 to 0.010 inch whereby, when pressure in said rotor chamber risesto a predetermined degree, hydraulic liquid flows over concave vanesurfaces to and between said rotor and said casing to convex vanesurfaces on the second rotor.
 4. Apparatus as in claim 3 wherein all thevanes and pockets in the second rotor are of the same shape and size onthat rotor.
 5. Apparatus as in claim 4 wherein the vanes and pockets onboth the first and second rotors are of the same shape and size.
 6. Atorque multiplier assembly comprising, in operative combination, 7.Apparatus as in claim 6 wherein said rotor casing has opposing parallelflat side walls and a cylindrical end wall enclosing a rotor chamber,said rotor assembly in said chamber and including a second flatseparator disk between one rotor body and one adjacent rotor casing sidewall and a third flat separator disk between another roTor body and anadjacent rotor casing side wall opposite to said first side wall, saidsecond and third separators each having an outer edge closer to thecylindrical interior casing surface than the radial edges of the rotorbodies.
 8. Apparatus as in claim 7 wherein all the vaned pockets in onerotor body are of the same shape and size.
 9. Apparatus as in claim 8wherein all the vanes and pockets in the second rotor body are of thesame shape and size on that rotor body.
 10. Apparatus as in claim 9wherein the vanes and pockets on both the first and second rotor bodiesare of the same shape and size.